Clutch structure for spinner type washing machines



v Oqt. 24, 1950- 1-, WQODSQN 2,527,238

\ CLUTCH STRUCTURE FOR SPINNER TYPE WASHING MACHINES Filed Aug. 25, 1944A 6 $heets-She'et l Inventor Thomas T Woodso'fl,

His Attorney i 1950 'r. T. WOODSON 2,527,233

' cw'rcn smuc'runs FOR sum TYPE WASHING lucamss Filed Aug. 25, 1944 6Sheets-Sheet 2 Inyentor Thomas T. Woodson His Attorney.

Oct. 24, 1950 1'. 'r. WOODSON 2,527,238 I CLUTCH STRUCTURE FOR SPINNERTYPE WASHING MACHINES Filed Aug. 25, 1944 v 6 Sheets-Sheet 3 T InventorT. Woodson,

His toorney.

Oct. 24, 1950 T. T. WOODSON' 2,527,233

CLUTCH smuc-ruas FOR SPINNER Tm: nsnmc ucumss Filed Aug. 25, 6Sheets-Sheet 4 Figll.

Inventor Thomas "I: \X/bodson His Attorney.

Oct. 24, 1950 T. T. WOODSON CLUTCH STRUCTURE FOR SPINNER TYPE WASHINGMACHINES Filed Aug. 25, 1944 6 Sheets-Sheet 5 Inventor Thomas T.\X/bodson,

Oct. 24, 1950 1-, WOQDSON 2,527,238

CLUTCH STRUCTURE FOR SPINNER TYPE WASHING MACHINES Filed Aug. 25, 1944 6Sheets-Sheet 6 Inventor": a2 5' Thomas TWoodson,

by WWQML H- Hi5 Attorneg Patented Oct. 24, 1950 CLUTCH STRUCTURE FORSPINNER TYPE WASHING MACHINES Thomas T. Woodson, Fairfield, Conn.,assignor to General Electric Company, a corporation of New YorkApplication August 25, 1944, Serial No. 551,096

Claims.

The present invention relates to washing and drying machines and isparticularly concerned with hydraulically controlled driving mechanismin which the motor, mechanism, and control may be enclosed within asealed casing.

The object of my invention is to provide an improved construction andarrangement in washing machines of this type, and for a consideration ofwhat I believe novel and my invention, attention is directed to thefollowing description and the claims appended thereto.

In the accompanying drawing, Fig." 1 is a sectional elevation of awashing machine embodying my invention; Fig. 2 is a bottom plan view;Fig. 3 is a section on line 9-4 of Fig. 1; Fig. 4 is a detail of thefloat controlling the liquid supply; Fig. 5 is an enlarged sectionalelevation of one form of the driving mechanism; Fig. 6 is a sectionalview on line 6-6 of Fig. 5; Fig. 7 is an enlarged view of the upper endof the agitator; Fig. 8 is a section taken on line 9-8 of Fig. '1; Fig.9 is a section taken on line 9--9 of Fig. 7; Fig. 10 is a detail of thepressure relief valve in the oil line; Fig. 11 is a section on line l|liof Fig. 5; Fig. 12 is a section on line l2--l2 of Fig. 5; Fig. 13 isanother modification of the driving mechanism; Fig. 14 is a modificationof the agitator driving gearing for slow speed agitator oscillation;Fig. 15 is a section on line Iii-l5 of. Fig. 14; Fig. 16 is a section online i6l6 of Fig. 14; Fig. 1'! is a detail of the adjustment of theoscillating sector gear; Fig. 18 is a detail of the upper end of theslow speed agitator.

Referrin to Fig. 1 of the drawing, there is shown a washing machinehaving an outer casing or tub I in the upper part of which is located aspinner basket 2 having centrifugal discharge openings 3 at the regionof greatest diameter which during washing are at or slightly above theliquid level." The spinner basket is non-rotatably seated in a carrier 4having annular walls I surrounding the basket and serving as a balancering and having radial arms 6 bolted to a hub I (Fig. 5) fixed by aclamp 8 (Fig. 6) to a tubular shaft 9 for supporting and driving thespinner basket. The space between the basket and the hub is sealed by arubber sleeve la (Fig. 5) having its upper end fixed to the hub and itslower end fixed to the basket. At-the upper end of the hub is a bearingin (Fig.

' 5) for the lower end of a bladed agitator ll fasand I30 in the spinnershaft 9. An oil retain- 2 ing felt ring ltd is associated with thebearing Illa. The shaft 13 has fixed thereto an agitator drive nut I4fitting in a complementary socket IS in the agitator hub. A shaft sealIla is provided between the upper ends of the spinner and agitatorshafts 9 and III.

In the agitator hub I 6 at or slightly below the wash water level in thespinner basket are drain passages 18 leading to the space between thespinner shaft 9 and the agitator hub it. The water draining throughthese passages flows through the space between the shaft 9 and theagitator hub and through passages H in the carrier hub 1 to the bottomof the outer casing I whence it is pumped onto an annular filter 2|(Fig. 1) on the rim of the spinner basket b a circulating pump 20 (Fig.2). The pump has its inlet (not shown) connected to the lowermost partof the casing and its discharge connected to a conduit 20a having anozzle 20b directed onto the filter. The pump is operated during washingso the wash water is continually withdrawn from the spinner basketthrough the passages I 9 and I9 (and possibly openings 3) and returnedto the basket through the filter 2|. the water removes lint and otherparticles and keeps the wash water clean. The amount of wash waterflowing through the passages l9 and I9 automatically adjusts itself tothe capacity of the pump 20 by slight variation of the wash water level.If the pump flow should become restricted, the wash water level wouldfall only slightly below the lower edges of the openings.

it which is only slightly less than the desired water level for washing.

There is also provided a drain pump 29c having its inlet (not shown)connected to the lowermost part of the outer casing l and its dischargeconnected to a conduit 20f leading to a drain above tub water level. Thepumps 20, 200 are driven by suitable separate electric motors, notshown.

The concentric spinner and agitator drive shafts 9 and 13 are driven bymechanism enclosed within a sealed casing 22 (Fig. 1) having its upperend projecting through openings 29 in the bottom plate 24 of the outercasing. The space between the casing 22 and the plate 2i is sealed by aflexible annular rubber ring 25 having its inner edge clamped to thecasing 22 and its outer edge clamped to the plate 24. The ring 25 isflexible to prevent the transmission of vibration to the outer casing.The upper end of the casing 22, which is above the maximum Thecontinuous circulation and filtering of.

water level in the outer casing l, is provided with a reduced hub 21(Fig. which projects within a skirt 25 at the lower end of the hub I andis provided with a seal 25 and a sleeve bearing 55 for the spinner shaft5. During both washing and centrifugal drying the upper part of the gearcasing 22 is cooled by the wash water. During washing, the wash waterfalls onto the upper end of the gear casing from the es I5. Duringcentrifugal drying, the wash water discharged through the centrifugaldischarge openms 3 falls into the bottom of the outer casing andpartially submerges the upper end of the gear casing. I

The driving motor 31a for the machine is carried in a frame 3| bolted tothe under side of a flange 25 at the lower edge of the gear casing 22and enclosed by a shell 32 (also bolted to the flange 25) which formsthe motor cover. The motor shaft 33 is journaled at its upper end in thelower half 34 of a rotatable frame 340. The

7 lower half 34 of the frame is journaled in a bearing 35 in the motorframe 3| and the upper half 35 being fixed to the spinner shaft 5. Theweight of the spinner basket and contents and of the frame 34a iscarried on a thrust washer 35s at the upper end of the bearing 35. Thelower end of the motor shaft 33 is journaled in a bearing 31 in theframe 3|. The lower end of the bearing 31 is provided with an eccentricbore 38 closed by a plate 35 and forming the housing of a vane typerotary oil pump. The oil pump housing is connected with a sump at thebottom of the shell 32 by a suction intake 45 and is provided with apressure discharge passage 4|. The rotor of the pump consists of theextreme lower end of the motor shaft 33 which is slotted to receivevanes 42 (Fig. 12) which are held by centrifugal force against the bore33. Integral with the upper end of the motor shaft 33 is a pinion 43meshing with a gear 44 shrunk on a hub 45 of a crank shaft 46 journaledin bearings 41 and 48 in the lower and upper parts 34, 35

of the rotatable frame 340. The crank arm 45 of the crank shaft isconnected by a connecting rod 55 to a pin 5! fixed between the forkedends 52 to the lower frame member 34. The member 55 loosely surroundsthe cup 58 so as to permit alignment of the brake surfaces 54 and 55,and the axial movement thereof is limited by a flange 59 on the cup 58.The lower end of the spring 5'! is seated on the bottom of the member 55and the upper end of the spring is seated on a thrust washer 60 clampedbetween the cup 58 and the lower frame member 34. The thrust istransmitted to the frame 3! through a thrust washer 55a at the lower endof the bearing 35. The braking or accelerating torque is transmittedthrough a structure comprising a hub 5i riveted to the washer 60 and thecup 58 and having curved axially flexible radially extending spring arms52 fixed to the member 55. When the brake surfaces are in engagement,the frame 34a (and the spinner basket 2 which is fixed thereto) isbrought to rest and the relative rotation of the motor shaft 33 withrespect to the frame 340 causes oscillation of the agitator at a speedof 4 the order of 350 oscillations per minute and through an arc of theorder of 60 degrees in the present construction where the motor is a6-pole induction motor having a full load speed of about 1150 R. P. M.The speed and stroke of the alltator obviously depend upon the motorspeed and the oscillating mechanism carried in the frame.

During centrifugal drying, the spinner basket 2 is clutched directly tothe motor shaft 35 by a conical clutch member 55 slidably surroundingthe motor shaft and fixed to the upper end of a bellows 54 surroundingthe motor shaft and keyed to the rotor 55 of the motor Ila by pro-Jections 55a on the bellows fitting in sockets 55 in the rotor. Thebellows is biased to the collapsed position by a coil spring 51 arrangedbetween the clutch member 53 and a washer 55 on the motor shaft.

The bellows is extended to move the clutch member 53 against acomplementary clutch surface 55 on the member 55 (and to lift the member55 clear of the brake surface 55) by oil pressure admitted throughpassages 15 in the motor shaft and through a port H in the plate 35. Theport H is normally closed by a spring biased plunger 12 of a solenoidvalve 13 mounted on the under side of the plate 55. Oil from the pumpdischarge 4| is conducted through a port 14 in the plate 35 to a chamberformed between a dished member 15 and the under side of the plate 35.

When the solenoid valve is energized, the plunger 12 is moved downward,opening the port II and admitting oil under pressure through thepassages 15 to the interior of the bellows and raising the clutch member53 into engagement with the clutch surface 55 (disengaging brakesurfaces 54 and 55) and establishing a friction drive from the motorthrough the spring arms 52 and the frame 34a to the spinner basket.While the spinner basket is being accelerated the clutch surfaces slipand there is relative rotation between the motor shaft 33 and the frame34a which causes oscillation of the agitator at a decreasing rate as thespinner basket approaches the motor shaft speed. As the clutch slippageapproaches zero, the coefficient of friction increases and the clutchsurfaces lock, placing a transient load on the motor which slightlylessens the motor speed. Thereafter the spinner basket runs at motorshaft speed which increases to the point on the motor speed torque curveat which the friction and windage load equals the motor power.Throughout centrifugal drying, oil is supplied to the bellows and leaksfrom bleeder openings 15. When the solenoid valve is deenergized, theoil supply to the bellows is cut of! by the closing of the port I! andthe bellows returns to the collapsed position in which the brakesurfaces are engaged and the clutch surfaces are disengaged. To preventexpansion of the bellows until the motor is up to speed, a centrifugalvalve 15a is provided which is moved outward by centrifugal force toclose a bleeder opening 15!: large enough to prevent the building-up ofa bellows operating pressure until the motor is up to speed. The valveis gravity-biased to the open position.

In addition to supplying the hydraulic control for the washing anddrying operations, the oil pressure is used to pressure lubricate thebearings and the oil from the bearings heated by friction losses in themechanism and by the losses in the motor is thrown from the bearingsover the inside of the casing for cooling purposes.Thelowershaftbearingflisfedfrom one end of a passage 11. the other endof which is connected through passages 13 and 13 to the bearings 36, 30afor the lower frame member 34. A pressure relief valve 114: (Fig. may beused if desired to limit the oil pressure. Leading from an annulargroove 8. in the frame member 34 is a vertical passage II having itslower end closed and its upper end connected to a transverse passage 32leading betweenthe upper motor shaft bearing and the lower crank shaftbearing 41. Drilledfpassages 83 in the crank shaft feed the upper crankshaft bearing 40 and through branch passages 33a (Fig. 11) also feed thebearings at each end of the connecting rod 50. Oil for cooling purposesis sprayed from a fitting 83b at the upper end of the passage 33.Throughout the interior of the casing there is during rotation of themotor an oil mist which settles on the inner surface of the casing ofthe motor and other parts of the mechanism. The oil trickles throughsuitable drain passages (not shown in detail) to the bottom of thecasing. Oil settling on the rotor 05 is thrown outward by centrifugalforce so there is only an oil mist in the air gap of the motor. A dam60a is provided on the stator 65b which holds oil in contact with thestator windings 850 which trickles throughthe stator winding slots (notshown). From the upper crank shaft bearing 43 a passage 84 conducts oilto the agitator shaft bearings I 3a, I31), I30 and to the spinner shaftbearing 30.

The mechanism is controlled through conductors leading throughglass-to-metal seals 33 (Fig. 12) in the shell 32 leading to the motorand solenoid valve. Washing is started by closing the motor circuit.Centrifugal drying is started by closing the solenoid valve circuit inaddition and is stopped by opening both the motor and solenoid valvecircuits. Because the shift to centrifugal drying depends upon oilpressure, the motor must be up to speed before the mechanism can beshifted to centrifugal drying. This prevents heavy starting loads on themotor. Because the mechanism and control are sealed within thisenclosing casing 22, 32, a lifetime supply of oil is sealed within thecasing so that further attention is unnecessary.

The modification shown in Fig. 13 differs from the previously describedconstructions in the arrangement of the mechanism and control within thesealed casing 22, 32. The motor shaft 33 is drilled to provide an oilpassage I38 which is fed from the discharge side of the pump 33-40through ports I31, I33 in the plate 33. Through connecting passages, theoil supplied through the passage I36 pressure lubrlcates the bearingsfor the motor and mechanism. The mechanism is substantially identicalwith that shown in Fig. 5 except that the thrust washer 33a is replacedby a tapered roller thrust bearing I33 at the upper end of the casingand oil under pressure is supplied through a passage I40 to the lowerend of the agitator shaft I3.

During washing, the rotation of the frame 34a is prevented by a conicalbrake member I fixed at its upper edge to an annular piston I42 in acylinder 543 in the motor frame H. The brake member is biased upward bycoil springs I43a fixed between the brake member MI and a ring I44 fixedto the motor frame. The brake member cooperates with a complementary annular brake surface I 45 fixed to the outer ends of radial fiat springarms I46, the inner ends of iii which are bolted to the under side ofthe frame member 34. In the uppermost (braking) P081- tion. the brakemember I lifts a conical clutch surface I41 clear of a complementaryclutch I43 fixed to the motor. In the lowermost (clutching) position ofthe brake member I, it is clear of the brake surface I43 and the clutchsurface I41 is urged into contact with the motor clutch I43 by thespring arms I40establishing a direct driving connection from the motorto the spinner basket.

The shift from washing to drying is controlled by a solenoid valve I43having a plunger I43a which normally closes a valve port I 30 in passage11. When the valve I49 is deenergized, the port I is closed cutting offthe oil pressure in the passages 11, 18 and the brake member I H isaccordingly raised by the springs Ilia to the uppermost or brakingposition, the fluid in the cylinder escaping through suitable clearancebetween the piston and cylinder. When in raised position, the frame 34ais held against rotation by engagement of brake member I with brakesurface I45, clutch surface I41 being-separated from motor clutch I48 sothe relative rotation of the motor shaft in the frame causes oscillationof the agitator for washing. When the valve I49 is energized, theplunger I49a opens the port I50 and the oil pressure admitted to thecylinder I43 moves the brake member I to the lowermost position and theclutch I41 is moved by the spring arm I46 into sliding engagement withthe motor clutch surface I40 to establish a direct drive from the motorto the spinner basket. During rotation of the spinner basket, theagitator will be oscillated at a rate dependent upon the relativerotation of the motor shaft with respect to the frame 34a. Oscillationsof the agitator cease when the spinner basket rotates at the motor shaftspeed.

In Figs. 14-17 is shown a low speed agitator oscillating mechanism(approximately 180 degrees stroke oscillations/minute) which can besubstituted for the high speed oscillating mechanism (60 degree stroke350 oscillations/minute) of Fig. 5. Correspondin parts are indicated bythe same reference numerals.

As in the previously described constructions, the frame 34a whichcarries the agitator oscillating mechanism is made in two parts, theupper part 35 being fixed to the spinner shaft 9 and the lower part 34being journaled in a sleeve and thrust bearing 30, 30a in the motorframe 3| pressure lubricated by oil from the passage 13. During washinthe frame 34a is held stationary. During spinning the frame is clutchedto the motor.

The agitator is oscillated by a sector gear I10 pivoted on a stub shaft"I having a reduced portion I12 eccentric to the shaft (Fig. 15) mountedin a boss I13 on the upper frame member 35. The sector gear meshes witha pinion I14 keyed on the lower end of the agitator shaft I3. The meshof the gears I10, I14 is adjusted by an adjusting arm I13 keyed to thereduced portion I12. By turning the arm I15, the gear I10 is movedtoward or away from the pinion I 14. when the proper mesh is secured,the arm I15 and the shaft "I are locked in position by tightening nutsI16, I11. This adjustment will be made ordinarily when the machine isbeing assembled initially. The gear I10 is oscillated by a crank arm I18connecting the gear I10 with a gear I19 journaled on a shaft I00 fixedin a boss IN on the lower frame member 34. The gear I18 is driven by apinion I82 (Fig. 16) in- 7 tegralwithagearlfljournaledonashaft I fixedbetween arms I" and Illa of a frame ll! bolted to the lower frame member84. The gear I" meshes with the pinion It on the motor shaft 33.

The lubrication is a combination of pressure and splash or drip. Thelower sleeve and thrust bearings 38. Ila are pressure lubricated by oilfrom the passages 18, it and I. The upper end of the oil passage II isconnected by a tube I81 to a fltting I" having a port I" spraying 011against the inner surface of the casing 22 for cooling purposes, a portIll feeding oil under pressure to the passage 84 for lubricating theagitator shaft bearings Ila, ilb, Ilc, spinner shaft bearing 30 and aport I feeding oil through a passage Ill to a trough or rmervoir I inthe upper frame member 35. The trough III has drain holes I" from whichoil falls onto the gears I10, I19, and bracket cup Ilib, each of whichis constructed to hold oil on its upper face which is fed to the gearingbearings through passages I95. The run-off and splash oil in the gearcasin is relied upon to lubricate the gear teeth.

Water is supplied to the machine through two solenoid thermostaticmixing valves I", I81 (Figs. 1 and 2) having flttings I", I forconnection with the hot and cold water supply lines. The valve I96 isadjusted to supply hot, and the valve I91 is adjusted to supply tepid,water. When both valves are operating, water of an intermediatetemperature is supplied. The temperature of the water may be controlledby suitable switch means, not shown manually adjustable to energizeeither or both of the solenoids IiISa, I91a for the valves I96, I91 toobtain tepid, hot, or intermediate temperature water, The tepid watervalve I91 has a discharge conduit 2M (Fig. 1) terminating in a nozzleIllla directing a stream against a splash ring or flange 202 projectinginwardly from the outer casing i slightly below the bottom of thespinner basket. The spattering at the desired time breaks up any soapsuds which may accumulate during washing and reduces the friction dragduring drying which in extreme cases might be enough to keep the basketfrom coming up to speed. The hot water valve has a discharge conduit 20!leading to a soap box 204 having a discharge nozzle 205 directed to thespace between the tank wall and the spinner basket. This soap box may besimilar to that disclosed in my application Serial No. 551,097, filedAugust 25, 1944. The soap box is arranged to receive granular or flakesoap which is flushed out of the soap box by the water and falls intothe bottom of the outer casing. The soap is thoroughly mixed ordissolved in the circulating pump 20 as the water is pumped from thebottom of the outer casing into the spinner basket. The hot water is ledinto the soap box through a tangential inlet 296 so as to set up avertical motion of the water which thoroughly washes the side walls ofthe soap box. The soap box discharge nozzle 205, which is open at alltimes, projects outward a sufiicient distance so that dry soap will notfall out due to the natural angle of repose of the soap. Water forwashing and rinsing is pumped up to the spinner basket 2 by thecirculating pump 20 and drips through the filter 2i, gradually reachingthe clothes in the basket and preventing ballooning (trapping of airbeneath folds of wetted clothes) which is accentuated by the dischargeof high velocity streams into the basket.

Thewaterisshutoilbyafloatili (HI-4) 11-sponsivetotheaocumulationofwsterinthebofi tom of the outer casing which,when the basket isfllledtooverflowingandasmallamountof water accumulatesin the casing, opens a switch III in series with the solenoid valves I","1. Float Iii may actuate additional switches if desired, it being shownin the present instance as actuating switches 2i; and I which may beswitches of a control system for the machine such as that disclosed andclaimed in my divisional application Serial No. 639,816, flied January8. 1946.

To prevent objectionable vibration during extracting, resilientmountings are provided which permit the basket to rotate about itscenter of mass and which damp the high amplitude mations associated withthe critical speed.

In the resilient mounting shown in Figs. 1 and 2, the spinner basket anddriving mechanism are supported by a plurality of coil springs 2 arranged between the under side of a flange II! on the lower half I! ofthe casing 22 and an inwardly extending flange 2 I6 (Figs. 2 and 3) atthe lower end of a cylindrical supporting member 2 I1 supported by thebottom plate 24 of the outer casing and depending through the opening23. The springs have a stiffness such that the critical speed is of theorder of R. P. M., or slightly above the water emptying speed of thespinner basket-the speed at which the free water in the basket (thewater not absorbed in the clothes) is centrifugally discharged.Suflicient clearance is provided to permit a lateral movement of thecasing 21 without striking the support H1 or the flanges 2I8. Fixed tothe flanges 2|! are horizontal arms 2i8 (Fig. 3) carrying pads offriction material Zita extending tangentially to the casing 12 betweenspaced vertical spring strips 2 I9 (Fig. 1) having the upper endspivoted in rubber sockets 210 on the flange 2 l 5 and having the lowerends urged together by springs 22!. The spring strips are bowed so thespacing varies along the length of the strips. The pressure on thefriction pads 2l8a accordingly varies with the position of the arms 2i!relative to the strips. When the basket is full of water, as it will beat the start of centrifugal drying, the arms III! are at the upper partof the springs strips II! where the friction is greater. This greaterfriction is helpful in damping the large amplitude vibrations as thespinner basket goes through the critical speed. After the basket isemptied, the weight on the springs I is materially reduced and the arms2 I8 are moved to the center of the spring strips 2I9 where a lesserfriction damping is exerted sufllcient to limit the amplitude of thevibrations in the speed range from the critical speed to the normalrunning speed. In addition to supplying the friction damping, the springstrips ii! are laterally yieldable as a pair to permit the lateralmovement of the gear casing 22 which is found to be helpful in reducingthe transmitted vibration. The lateral movement of the gear casing atthe location of the friction dampers 2l8, 2l9 permits lowering of thenode of vibration below the spring support so that less angularity ofthe spinner shaft is required to permit rotation of the spinner basketabout its center of mass.

In Fig. 13 is shown another form of resilient support applicable to eachof the machines. In

this construction the bottom plate 2i of the outer casing has anupwardly extending cylindrical pedestal 222 having an inwardly extendingflange aromas 2220 at the top spaced from the sear casing 22 to which issecured a supporting member 223 having an upwardly presented sphericalsurfac 224 carrying spherically surfaced friction material 225. Asupporting member 228 bolted to the upper end of the casing 22 has aconcave concentric spherical surface 221 seated on the frictionmaterial. The casing is resiliently centered in an upright position by arubber ring 22: arranged between a flange 22! on the casing 22 and theunder side of a flange 230 on the supporting member 223. The rubber ringis keyed to the flanges 220 and 230 and is under compression providing,when casing 22 is angularly displaced, the pressure between the surface221 and the friction material 225 necessary to damp th gyratoryvibration of the gear casing and spinner basket. The stiffness of therubber ring is such that the critical speed is of the order of 100 R. P.M. and the friction damping exerted by the friction material 225 issuflicient to limit the amplitude of the gyration at the critical speed.with this construction, the basket and gear casing gyrate about thecenter of the spherical surfaces 224, 221 (the node of the vibration) toan extent sufllcient to permit the spinner basket to rotatesubstantially about its center of mass, thereby minimizing the vibrationdue to unbalanced distribution of clothes in the basket.

What I claim as new and desire to secure by Letters Patent on the UnitedStates is:

1. In combination, a spinner basket. shaft, an agitator shaft, drivingmechanism having s. rotatable frame for driving the spinner basketshaft, a driving shaft journaled in said frame, mechanism operated byrotation of said shaft relative to said frame for driving the agitatorshaft, clutch and brake means surrounding said drive shaft andresiliently connected to said frame in spaced relation thereto forclutching the frame to the drive shaft and for braking the rotation ofthe frame, said means including an axially movable member and a bellowssurrounding the shaft to which it is fitted, means biasing said axiallymovable member to the braking position, a passage for supplying fluid tothe bellows to effect movement of said member from the braking position,and means controlling the supply of fluid to said passage.

2. In combination, a pair of shafts, a frame connected to one of saidshafts for rotation thereof, gearing carried by said frame through whichthe other shaft is operated, a brake shoe flxed relative to said frame,a motor, means connecting the motor to said gearing, a clutch memberflxed to said motor, a combined brake and clutch member, arm meansflexibly connecting said frame and said combined brake and clutch memberfor movement of the latter axially relative to said brake shoe, springmeans effecting a, braking engagement between the brake shoe and thecombined brake and clutch member and establishing a position of saidlatter member out of engagement with said motor clutch member, a fluidpressure actuated member for releasing said braking engagement andconcomitantly effecting engagement of said motor clutch and saidcombined brake and clutch member, and means for supplying fluid pressureto said fluid pressure actuated member.

3. A unitary structure for actuating two shafts comprising a sealedcasing, a vertical shaft motor in the casing, a frame in the casingabove the ably aflixed to said frame, said structure when motorconnected to one of said shafts, an axially movable unitary brake andclutch structure yieldin one position braking said frame anddisconnecting it from the motor and in another position releasing theframe and cmmecting it to the motor, actuating mechanism carried by theframe through which the other of said shafts is connected to the motor,a pressure actuated member for moving the brake and clutch structure,and a pump driven by the motor for supplying fluid pressure to saidpressure actuated member.

4. A unitary structure for actuating two shafts comprising a sealedcasing, a vertical shaft motor in the casing, a frame in the casingabove the motor connected to one of said shafts, an axially movablebrake and clutch structure resiliently connected to said frame, saidstructure when in one position braking said frame and disconnecting itfrom the motor and in another position releasing the frame andconnecting it to the motor, spring means biasing said structure intobraking position, actuating mechanism carried by the frame through whichthe other of said shafts is connected to the motor, a pressure actuatedmember for moving the brake and clutch structure, a pump driven by themotor for supplying fluid pressure to said pressure actuated member, andan electrically operated valve controlling flow of fluid from the pumpto the pressure actuated member.

5. In combination, a spinner basket shaft, an agitator shaft arrangedcoaxial therewith, means including a. rotatable frame for driving saidspinner basket shaft, a driving shaft journaled in said frame, mechanismoperated by rotation of said driving shaft relative to said frame fordriving the agitator shaft, a, brake member concentric with respect tosaid frame, means for securing said brake member against rotationrelative to said frame, a unitary clutch and brake means concentric withsaid drive shaft, arm members securing said unitary means to said framefor axial movement relative thereto, said arm members biasing saidunitary clutch and brake means and said brake member releasably intoengage ment, a motor for said drive shaft, 9, fluid pump driven thereby,a clutch member coaxial with and driven by said motor for transmissionof motor power to said unitary clutch and brake means, means disposedabout said drive shaft and responsive to application of fluid pressurethereto for movement coaxially of said shaft for effecting adisengagement between said brake member and said unitary clutch andbrake means and. connection of the clutch portion of said last-namedmeans with said motor driven clutch member, flow .passage meanscommunicating between said pump and said pressure responsive means, aby-pass from said fluid pump, and valve means for optionally by-passingpump discharge relative to said pressure responsive means or fordirecting said pump fluid pressure thereto.

THOMAS T. WOODSON.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Name Date 427,085 Jones May 6, 18901,510,943 Kjelsberg Oct. '7, 1924 1,518,360 Royce Dec. 9, 1924 1,730,270Friedell Oct. 1, 1929 (Other references on following page) games 11UNITED STATES PATENTS Number 3,821,821 Number Name Date m 158 1.753.370Olsen m 13, 1930 48's 3 .10 Wemp Nov. 7, 1933 2,617 Wood Jan. 9, 1934,069,408 Fortchon Feb. 2, 193'! ,643 Gmett July 20, 1937 Numb. D60. 5,8,068 Fawlck Mar. 31, 1942 10 2,800,421 Henderson Nov. 3, 1942 Name Datemum- June 15, 1943 Dyer Apr. 11, 1044 Dunhorn Apr. 18, 1944 Dnehoua June20. 1944 FOREIGN PATENTS Country Date Bwlturhnd A118. 1, 1917Certificate of Correction Patent No. 2,527 ,238 October 24:, 1950 THOMAST. WOODSON It is hereby certified that error appears in the printedspecification of the above numbered patent requiring correction asfollows:

Column 9, line 44, for the Word fitted read fixed; line 47, after saidinsert am'ally movable;

and that the said Letters Patent should be read as corrected above, sothat the same may conform to the record of the case in the PatentOflice.

Signed and sealed this 20th day of March, A. D. 1951.

THOMAS F. MURPHY,

Assistant Commissioner of Patents.

Certificate of Correction Patent No. 2,527,238 October 24, 1950 THOMAST. WOODSON It is hereby certified that error, appears in the printedspecification of the above numbered patent requiring correction asfollows:

Column 9, line 44, for the Word fitted read fixed; line 47, after saidinsert axially movable;

and that the said Letters Patent should be read as corrected above, sothat the same may conform to the record of the case in the PatentOfiice.

Signed and sealed this 20th day of March, A. D. 1951.

THOMAS F. MURPHY,

Assistant Commissioner of Patents.

